Vane pump



Oct 19,1943. J. s. WENTWORTH VANE PUMP Filed May 25, 1939 5 Sheers-Sheetl v INVENTOR. Jesse S. WENTWORTH,

r I ATTORNEY Oct. 19, 1943. .1. s. WENTWORTH VANE PUMP Filed May 25,1939 5 Sheets-Sheet 2 INI'ENTOR. JESSE S. WENTWORTH,

ATTORNEY 1943. .1. s. WENTWORTH 2,331,878

VANE PUMP Filed May 25, 1959 5 Sheets-Sheet 3 INVENTOR. JESSE S.WENTWORTH ATTORNEY v 9 1943- J. s. WENTWORTH I 2,331,873

,VANEPUMP 7 Filed May 25 1959 5 Sheets-Sheet 4 5 52.1 I 3.1211. 147 IINVENTOR.

JEssE S. WENTWORTH,

Egg? mg?? Patented Qct. re, 1943 VANE PUMP Jesse S. Wentworth,Cincinnati, @hio, assignor to Wentworth and Hull, a mutualcat-partnership composed oi Jesse S. Wentworth and Bertram G. "Hull,Cincinnati, (Ohio a Application May 25.1w, Serial No. was

8 Claims. (6i. 230-439) I y This invention relates ,to improvementsinpumps, such as are used in connection with me chanical or electricalrefrigerators,,for delivering fluid or gas under pressure, and forsimilar purposes. I

One of the principal objects of this invention is the provision of sucha pump, which is ,com-

pactin size and relatively inexpensive to manu-.

facture, yet highly eficienttin operation.

Another object of this invention. is the provi sion of a pump in whichthe friction between- 1 moving parts is reduced to a minimum, therebyreducing wear between the parts and materially 1 extending the lifeofsuchpumps. A further object of this invention is the prosubstantiallywithout packing, and in which'the parts are so related to one another asto prearound the pump shaft. I

A still further object of this invention is. the provision of a pumpto-be used as a compressor vent leakage and losses, despite .no packingin connection with mechanical andeleetrical re- 'frigerators, and inwhich solid particles and glob:

ules of oil are removedfrom the gas before the compressed' gas isinjectedinto the compressed gas line.

A still further object of this invention is to arrange thepump and itsdriving means with respect to.one another, whereby only the heighth ofone of these members is required to take in both the pumpand itsdrivingmeans.

A stillfurther and'specific object {of this-inq vention is the provisionof'apump as above re-' ferred'to, in which the friction is reduced toaminimum, in that only an oscillatory, sliding- '15 Vision of a'pump as'above-described, which is pump is'started, and the pressure then raisedto a maximum after the pump is running.

Other objects and advantages of the present j I invention should bereadily apparent by refer- .ence to the following specification,considered in conjunction with the accompanying drawings forming a partthereof, and it to be understood that any modifications may be made inthe exact structural details there shown and described,

within the scope of the appended claims and without departing from orexceeding the spirit of the invention.

' In the drawings:

Fig. 1 is a vertical, sectional view through a combined pump and motor,assembled in its -pre ferred form.

5 Fig.- 2 is anelevation aliview of: the pump of Fi .1, as seen, from'thebottom thereof.

Fig. 3 is' a horizontal, sectional view,.take'n on line .of Fig. .1.

Fig. 4 a, horizontal, sectional View, taken on i 3 line sg-s of Fig.1..

v 'Fig. 5 'is' airagmentary, horizontal, sectional view, takenin-a.plane below Fig.4 and showing the parts in a second position ofadjustment.

, -Fig. 6 is;a fragmentarm seotional view,'showv Fig. 1.

,Fig. :7 is an" enlarged, horizontal, sectional view,

ing partsin elevation, and taken on line 6+6 of contact between therotor and its housing-is had,

instead of a constantly running -'e ngagement..

Itis also an object of this. invention to pro;

errors in manufacture, and alsoto take up pos-- siblewear between theparts.

A still further object of this invention is the .vide an adjustingmeans; for adjusting the throw: i of the eccentricto take care ofpossible 'small- .lower end :uti lized in this Fig. 8 is a vertical,sectional view through the,

of Fig. 1 and taken1on;line 8'8 of F 1 Fi 9'is:a perspective view ofthepump Wing lustrated on an enlarged scale over-that shown n the otherviews.

Figaro is a v'erticalfsectionalviewthrough pump and its" drivemotor,illustrating amodification therein.

Fig. .11 is a. transverse, .sectionaliview,taken .pr'ovisiono'i a pumpof the class above. referred to, wherein the'eccentric throw of the pumprotor may be varied'o'r adjusted to increase and de- I crease pressurethereof on'the housing, and wherein-this decrease is employed to=reducethe starting torque necessary ininitially starting .the pump,-' I

It is also an objectofl'this invention to provide a pump-whereinthepressure between the pump; rotorand its housing is reduced to zerobefore the I Fig. 121s a fragmentary. horizontal, sectional v Fig. 13 isa=fragmentary,. sectional view, taken.

'Fig. 14 is an frag'mentaryy vertical sectional vi'ew,- tak'en, on lineNi l-4 of'Fig. I3. 'Fig.- 15, is a verticah sectional 'VlCW, similar toFigsullzandlm-throiigh a pump'and its drive motor, illustrating furthermodifications in the construction and operation thereof.

Fig: 16 is aihorizontal, .sectional view, taken v.online ifi lfiof Fig.15. 3 I v f application,- said wing being ,il-'

Fig. 1'1 is a fragmentary, horizontal, sectionalview, taken on line |1|1 of Fig. 15.

Fig. 18 is a view, similar to Fig. 16, taken in a plane below that ofFig. 16, on line |8|8 of Fig. 15.

Fig. 19 is a vertical, sectional view, on an enlarged scale, of the pumpmechanism of Fig. 10, and showing certain modifications therein wherebythe throw of the pump impeller may be adjusted.

Fig. 20 is a transverse, sectional view of a portion of the disclosurein Fig. 19, taken on line 2|12|l of Fig. 19.

Fig. 21 is a view similar to that shown in Fig. 20, with the parts in anadjusted position to one side of that shown in Fig. 2-1.

Fig.22 is a view similar to that shown in Fig. 21, with the parts in theopposite position of adjustment.

Fig. 23 is a bottom plan view of the pump mechanism of Fig. 19, taken online 23-23 of Fig. 19, showing the means for obtaining the adjustmentsof Figs. 20, 21 and 22.

Fig. 24 is a view very similar to that of Fig. 23, showing the means forautomatically effecting the adjustments of Figs. 20, 21 and 22.

Fig. 25 is a wiring diagram showing the connection of the motor fieldsand solenoid employed in effecting the automatic adjustment of theparts.

Throughout the several views of. the drawings, similar referencecharacters are employed to denote the same or similar parts.

As was noted above, this invention pertains to a pump for use inconnection with mechanical or electrical refrigerators, and similarpurposes,

where it is desired to compress gases or fluids or to transfer liquidsor fluids under pressure. It is also one of the chief purposes of thisinvention to supply such a pump or compressor unit in which the partsare intimately associated with one another and enclosed in substantiallya single housing, whereby the manufacturing costs may be materiallyreduced and required accommodating space likewise reduced to a minimum.

Specifically referring to the drawings, and particularly to Figs. 1 to 9inclusive, which illustrates the preferred embodiment of this invention,it will be noted that use is made of an upper housing 25 and a lowerhousing 26. These housings are substantially cup shaped and have,respectively at their adjacent ends, radial flanges 21 and 28, throughwhich pass looking or clamp screws or bolts 29. If desired, a" gasket(not shown) may be inserted between said flanges for making the interiorof the housings air and gas tight to the exterior. In addition, each ofthe housings 25 and 25 have projecting from their outer surfaces, fins30 and 3| for radiating heat generated and developed within thehousings.

The upper housing 25 is counter bored to provide a shoulder or seat 32;against which the motor field laminations 33 abut, and the seat 32 formsa shoulder which, along with the inner overhanging portion 34 of radialflange 28, affords means for clamping 'the motor field laminations inposition. Associated with said laminations, as is usual practice, is themotor field coil 35. Secured to the upper housing 25, and passingthrough the wall thereof, is a sealed-in plug or connector 36, throughwhich the external elec-' tric source or wires 93 is connected with themotor field coil 35.

Centrally of the motor field laminations 33 are the armature laminationsshown here as secured over the pump assembly, and indicated in generalby the reference numeral 31. In other words, the motor armature hasbuilt within its center the pump or compressor, whereby the rotation ofthe motor armature operates the pump. The pump assembly 38 comprises acentral pump cylinder 39 in the form of a ring or sleeve, having securedto its upper end a plate 48, and to its lower end a second plate 4|. Theplates 40 and 4| respectively have projecting outwardly thereof bearingsor trunnions 42 and 43, respec tively received in inwardly projectingbearing bosses 44 and 45, formed integral with the housings 25 and 26,and projecting toward one another. The plates 48 and 4|, and theirrespective sleeves 42 and 43, are each provided with a bore in axialalignment, and which bores are concentric with the inner housing sleeve39 when in assembled position. The securing of end plates 40 and 4| tosleeve 39 provides, interiorly of said sleeve, a chamber 46 in which isdisposed the pump rotor 41, which is in the form of a sleeve, centrallybored and having an external diameter less than the internal diameter ofthe cylinder sleeve 39.

Disposed in the bores of closure plate sleeves 42 and 43 are the endsofa shaft 48, which has its such that the rotor 41 has at all timestangential line contact with the inner surface of the cylinder ring 39or chamber 46, as seen clearly in Figs. 4 and 5. It will be noted thatthere is no positive connection between the shaft 48 and rotor 41,since, in fact, and as will later appear, the shaft 48 is always heldstationary, and the rotor is loose thereon.

In order to hold the shaft 48 stationary, the upper end thereof, seeFig. 6, is formed to provide a pair of flats 50 which are received in anaperture, having the cross section of the end of the shaft, and formedin a lever or wrench 5|. This wrench, see Fig. l, is located within acavity 52, formed within the bearing boss 44 and in the main lies abovethe upper surface of closure plate sleeve 42. Referring again to Fig. 6,

the wrench or lever 5| has, at its other end, an

aperture 53, through which passes a clamp screw 55, threaded into thebase of the cavity 52 and therefore into the stationary bearing lug 44.From the description just given, it will be noted that the wrench orlever 5| holds the shaft 48 against'rotation. It will also be noted thatthe pump cylinder 39, and end closure plates 40 and 4| are rotatedaround the shaft 48, particularly around the eccentric portion 49thereof, as is also the rotor member 41.

In order to rotate the rotor member 41, it is connected with the pumpcylinder 39 by a pump wing or vane 58, shown most clearly in Fig. 9, andshown in two operative positions in Figs. 4 and 5. As will be seen, thewing 58 has a hinge connection with both the cylinder member 39 and therotor member 41, and for this reason the wing or vane 58 is provided atopposite ends with ,hinge portions or knuckles 59 and 60, respecing withthe cavityEZ.

- and 26. wise in communication with the cavity ,52; throughvertical andradial bores or ports 86 crosses the chamber 36, dividing same into apair communicated with a groove 65 formed'circumferentially andexteriorly in the eccentric portion. of the shaft at a point near theupper end thereof. Extending from the groove 66 into the shaft is a port6? which communicates with a vertical port or bore -8-8 in said shaft,which has its lower end closed and upper end communicat- Likewise, theintake or suction chamber 36" has extending from it, through the pumpmember, a port 69 which communicates with'a groove i8 formedcircumferentially and exteriorly of-the eccentric portion of the shaftata point near the lower end thereof. This groovejfl communicates througha port ll with a verticalport or bore 12 in the lower end dial flange90, stopping short of the bearing boss 6G to provide a passage way 9!.

It should be noted that the interior of the housing 25, above the motorla'minations, forms a pressure chamber, while the space below the saidlaminations forms alubricating oil chamber with these chambers insubstantial unrestricted communication by way of the bores 89 and thenecessary clearance between the rotor laminations and fieldlamiriations' It should also be noted that oil for lubricating thebearing sur-' faces of the running parts is fed into the supply port andcarried to these surfaces by the gases and fluids being circulated. Forthis purpose,

use is made of a small pipe 92, connecting the .oil chamber, or lowerend of the housing, with the supply-port id.

The operation of the pump is as, follows:

The electric power is supplied I through the" lead wires 93, through theplug 36, to the motor field ,coil'for energizing same and causing therotation of the motor armature 37. Since this armature has securedthereto the pump mechaof the shaft, -and which bore or port '72 has itsupper end closed and its lower end communicating with a cavity 13,located below the shaft 48 and within the closure plate sleeve 43. Itwill be noted that this pump shaft is, to all intents and suitable ordesirable construction. As shownin the drawings, the check valve 15 isconical shaped, having extending therefrom a stem 76 shaft 38.

nism, thepump is rotated therewith about the the pumriqnechanism torevolvearound its eccentricportion 39. The rotation of the pumpmechanism around the eccentric, portion Moi the shaft, causes. the pumprotor M to roll its .outer periphery on the inner periphery of the pumpcylinder 39 in much the same manner that a small planetary gear wouldroll within an internal gear.

Since, however, the pump rotor and cylinder ring are connected with oneanother by the wing or vane 58 against independent rotation,

these members rotate as a unit, with a slight slippage therebetween. V

As will readily be appreciated, this slight relative movement causes thewing or vane 58 to move from the position illustrated in Fig. 5 to theposition illustrated in Fig. 4, and then back again to the position ofFig. 5 during each rotation oi the pump mechanism, and therefore of themodisposed for guiding purposes in a spider J'H located within thecavity 13 and below the shaft 48.

Between the valve 75, and surrounding the valve stem 16, and the spiderTi is a spring 18, which abuts on one end'with the spider I1 and ontheother end with the'valve 15 for atall times urging the check valve toa closed position.'

Between the cavity 52- and the vertical discharge or compression port 68is a check valve ,1 9, similar in all respects to thecheck valve [5,andlikewise' spring loaded. The stem of check ivalve l9 is mounted-forguiding purposes, in a the plate 80 is aring"83, having formedtherethrough radial bores 84, whereby communication between the cavity8| may be had through bores or ports 85formed vangularly througlr thebear.

ing boss 4,4,.with the interior of the housings 25 The. interiorofthehousings is likeformed in the bearing boss 44.

- On the upper surface of the motor rotor laminations 3'! are a pair ofbaflies 81 and 88, respectively circular and disposed at diametricallyoptor rotor. This causes an increase in the suction chamber 46" and acorresponding reduction of the discharge or compression chamber 46',thereby creating a suction or vacuum in the chamber 46", which unseatscheck valve I5,

- drawing gas or fluid throughthe' port Hand ejecting same from thechamber 66', thereby unseating the check valve- 19 and filling thecavity 52. The compressed gases and fluids in the cavity 52 pass downthroughfvertical and radial ports 86, and are discharged against thebafile 81. This baffle 81 causesthe gas or fluid to slide thereover andhave the oil suspended therein removed whereupon the gas or fluidengages the baffle 88-90. In striking the-baflies 81 and 8890,

practically all of the oil supplied to the gas and fluid by way of pipe92 is centrifugally removed therefrom, thereby completely removing anysuspended oil or moisture from the gas or fluid, and

providing substantially oil free compressed gas which flows from thebaflies through the pasposite points of vertical bores or apertures 89formed through the rotor laminations. baffle 88 is provided at its upperendwith a ra- The.

This oil or, fluid collects on the inner surfaces of the baffle Ala-90and flows downwardly wardly through bafile outlet 9| into-the pressurechamber, where it flows through the angular ports and ring ports 84 intothecavity 8!. The gas and fluid escapes from the cavity 8| Theshaft Q8,being stationary, causes ed with the supply port 14, andthis vacuum islikewise in the said port I4. With the motor and pump quiescent, thisvacuum will tend to suck the oil from within the housing 26 into the gasor fluid supply tank, and gravity fiow of the oil to the lowest pointmay drain all the oil into the supply tank. In order to prevent this, acheck valve is placed in the port I4 at the most convenient or desirablepoint, which is shown in the drawings as at the end of this port. Thischeck valve, indicated in general by the reference character I29, maytake any desirable or acceptable form, and that shown in the drawingscomprises a nipple 95, threaded into the end of the port I4, which has apassage therethrough and at the same time forms a seat for one end of aspring 96 which bears on its other end'against a ball valve 91. The ballvalve 91 is held to a seat at the inner end of a port 90, formed througha coupling 99, which is in turn threaded onto the nipple 95.

It will be readily appreciated that the cessation of suction in thesuction chamber 46" will allow both the check valve I5 and ball check 91to seat, thereby stopping any return flow in the suction system of theline, and any lubricant or oil that is in the housing 26 will flow bygravity into the port 14 between these check valves and will not bedrawn into the supply tank.

With this construction, also, when the motor is again. started, andthereby the pump, the first flow through the system is lubricating oil,which floods all of the rotating parts, and by supplying bearings ortheir bushings with suitable oil feeding grooves, the lubricating oil isdistributed throughout the running bearing surfaces, and since the oilis almost immediately supplied to these bearings upon the starting up ofthe motor and the pump, the bearings are without lubricant atsubstantially no time during their rotation.

As is usual practice, and in order to hold the temperature of the pumpor motor to a minimum at all times, both the upper and lower housings 25and 26, as above indicated, are respectfully provided with radiatingfins 30 and 3I substantially throughout their exterior surfaces.

In the mechanism just described, the pump and its prime mover are builtone within the other, while in the modified construction disclosed inFigs. to 14 inclusive, the pump and motor structures are builtindependently of one another, and subsequently secured to one another,but including the same principles of construction and operation.Specifically referring to the construction disclosed in Figs. 10 to 14inclusive, use is there made of a housing 25', in which is mounted themotor field laminations 33 shown as disposed between the shoulder 32within the housing 25' and the upper end of a pair of pins I02 whichupstand from a plate I03 partly disposed within the housing 25'. The

' motor rotor laminations 31, instead of being secured to the pumpcylinder, are secured in the usual manner to a motor shaft I04 which hasits upper end joumaled in a bearing boss I05. The lower end of the shaftI04 is journaled in a bearing boss I06 integral with the plate I03, andthis hearing being shown in the drawings as including a bearing bushingI01 carried by the boss I05 and receiving the lower end I08 of the shaftI04.

An outer pump housing casting 26 is utilized and has at its upper endthe radial flange 28 which engages a radial flange 21 at the lower endof the motor housing 25', and these flanges are secured to one anotherby the connecting screws or bolts 29, and between them the usual gasketfor sealing this joint. The said connecting screws or bolts provide theclamping pressure for holding the field laminations 33 in compressedsuperimposed position between the upper ends of the pins I02 and thehousing shoulder 32, since the plate I03 is secured as by clamp boltsI09 to the casting 26'.

Secured to the undersurface of the plate I03, as by bolts or screws H0,is a sleeve III carrying at its other end a bearing plate II2. Withinthe sleeve III.is the pump cylinder sleeve 39 which carries at itsopposite ends closure plates 40 and 4|, from which respectively projectthe trunnions or bearing sleeves 42 and 43'. The sleeve 42', in additionto forming interiorly thereof the bearing for the pump shaft 48, formsadditionally a clutch or connection with the motor drive shaft I04. Thisclutch is clearly shown in Fig. 12 and has several. clutch teeth II3projecting therefrom intermeshing with similar complementary clutchteeth II4 formed on the lower end of the motor drive shaft I04.

Within the pump cylinder 39 is the pump rotor 41, connected with thepump cylinder by the double hinge wing or vane 58, and which operates inthe same manner as that above described, and is rotated through thedrive of the pump cylinder about the eccentric portion 49 of the shaft48. The internal construction of the shaft 49, in Fig. 10, issubstantially identical with that disclosed in Fig. 1, except that theends of the shaft are provided with counter bores in order that theintake and exhaust valves respectively I5 and I6 may be positioned muchnearer to the intake and supply ports respectively 69 and 55, so as toreduce any possible re-expansion in the gas during the cycle of thepump. The discharge port 69 in thepump shaft 48 connects with abore II5formed through the center of the plate trunnion and bearing sleeve 42',and motor shaft I04 connected with a cavity IIS formed within thehousing bearing lug I05. This cavity II6 has its upper end defined by animperforate plate II'I held to its seat within the cavity by a cap H8and lugs II9 projecting therefrom. The cavity H6 communicates with theinterior of the housing 25' by way of ports I20 with the baiiles 81 and88-430 in the path of flow therethrough. The interior of the housing 25'communicates by wayof angular ports I2I with a chamber or cavity I22formed between the above mentioned irnperforate plate In and closure capH8, and this cavity I22 communicates with the discharge or pressure port94 and a pipe or conduit (not shown) connected therewith. a

The interior of the housing 25' communicates with the interior of thehousing 25' by way of vertical ports I23 formed through; the plate I03,

- the motor rotor 31.

and which ports deliver the separated lubricating oil into the housing26' for injection into the system inthe same manner as above described.

The shaft 48, in Fig. 10, similar to said shaft in Fig. 1, is heldstationary by a lever or wrench I24 connected therewith in the samemanner as the lever or wrench key I and locked in position by a screw orbolt I25 passing into the bearing plate H2. The lower bored end of theshaft -48 projects beyond the lever or wrench I24 into a coupling I26which has connected therewith one end of a tube I21 lying below thebearing plate H2, and which tube takes the place of the supply port I4,and is connected with the supply tank (not shown). A small bleed holeI28 is formed through one wall of the tube to provide for the injectionof the oil into the system. The tube I2! is projected, at a suitablepoint, through the wall of the housing 26' and has connected therewiththe oil check valve I29, which may be of any suitable or desirableconstruction, such as above described.

In order to prevent the shifting of the motor field laminations 33, aconstruction similar to that illustrated in Figs. 13 and 14 may beemployed, wherein a pin I32 is arranged half within the inner wall ofthe housing 25 and half Within the field laminations 33. In order thatthis pin I32 may be removed, in the event it is desired to take out thefield laminations, it is provided with a finger hold or shoulder I33.

The operation of the combined motor and pump structure in Figs. to 14inclusive is substantially identical with that above described inconnection with the structure in Figs. 1 to 9 inclusive. In other words,rotation of motor armature 37 carries with it the motor shaft I04,which, through its clutch connection II3II4 with the pump cylinder 39,rotates this housing.

The rotation of the pump housing 39, through the.

double hinge vane 58, rotates the pump rotor, thereby effecting apumping and compressing action through the pump.

The path of flow is from the supply tank (not shown), oil check valvemechanism I29, pipe or ciiuduit I21, port in the lower end of the shaft48, check valve 75, radial ports 69 into the chamber 46'. her, whenconverted into the compression cham ber 46', through the radial port 65,vertical port 68 in the upper end of shaft 48, past the check valve I6,port H5 in the closure plate trunnion and bearing sleeve 42 and motorshaft I04, cavity IIG, vertical ports I20, interior of housing 25',angular ports I2I, cavity I22 and exhaust port 94 and conduit andstorage tank (not shown) connected with the port 94. The flow of fiuidfrom the supply tank to the pump supply chamber 46" carries with itlubricating oil drawn through bleed hole I28 in the pipe or conduit I21.The fiow of the compressed gas or fluid from cavity II6 to the cavityII! is by way of baffles 87 and 88--90 for removing the lubricating oiltherein as above described, and for directing the lubricating oilthrough the vertical bores 89 in This separated lubricating oil fiows byway of ports I23 to the interior of the housing 26 and is collectedtherein, as well as in the inverted cup shaped lower housing closureplate I30 secured to the open end of the lower housing by means of boltsor screws I3I.

In connection with the construction just described and illustrated inFigs. 10 to 14 inclusive, it should be noted that the use of the clutchI I3-I I4 between the motor shaft I04 and driven The pressure flow isfrom this champump member 39 is advantageous in compensating for slightinaccuracies in the manufacture of the several parts, should they not bein absolute axial alignment and slightly out of line. It should also benoted that the mounting of the closure plate bearing on the trunnionsleeves 42 and 43 is in the same manner as above described, so that theshaft 48 may be angularly adjusted to compensate for wear and slightinaccuracies in the alignment of the parts.

In the modifications above described, the pump cylinder ring was drivenby the prime mover, which, through its connection by the double hingevane, effected the rotation or drive of the pump rotor. It has beenfound that substantially the same results can be obtained by driving theshaft and holding the cylinder ring stationary and allowing the pumprotor to roll within the cylinder ring and this rolling effected by theeccentricity of the shaft.

This latter construction is illustrated in Figs.

15 to 18 inclusive, wherein use is made of the same motor drive asdisclosed in Fig. 10, and for a description of which reference to theabove may be had. As shown in Fig. 15, the pump shaft 48" is provided atits upper end, see Fig. 17, with clutch teeth I34 which intermesh withthe clutch teeth H4 at the lower end of the motor shaft I04. Theeccentric portion 49" of the shaft 48 is encircled by the pump rotormember 535 disposed within the pump cylinder sleeve I36. The pumphousing sleeve I36 is connected with the rotor member by the doublehinged vane 58 in the same manner as above described, but this pumpcylinder sleeve I36 is secured against rotation by screws or bolts I31passing through the plate I03 into the upper end of the sleeve I36.

The sleeve I36 is encased in a casting or lower housing member I38, andwhich housing member has formed at its lower end a. supply port I39communicating with a vertical bore or port I40 in the lower end of theshaft 48". At the outer end of the port I39 is the oil ball check valveI29.-

The upper end of theshaft 48" is provided with a vertical port I4I,which communicates with the port II5 formed centrally of the motor shaftI04. The pump shaft ports I40 and I 4| are respectively in communicationwith the chambers in the pump cavity by way of ports I42 and I43,respectively, through the shaft 48" and adapted to be connectedrespectively with ports I44 and I45 formed through the pump port I43 hasconnected therewith the open end of a groove I46 formed through aportion of the periphery of the eccentric portion 49" of the shaft, andwhich groove terminates in a shoulder I41. The port I42 likewise hasconnected therewith the open end of a groove I48 terminating at itsother end in a shoulder I49. From this it will be seen that there is ablank space between the ends or shoulders of these grooves and theirports which out off any flow through the pump rotor ports I44 and I45during a portion of each rotation of the pump drive shaft.

By this construction, the compression in the pump pressure chamber 46'is built up to the pressure in the pressure receiving tank before anyadditional compressed-gasis forced thereinto, and a suction is createdin the chamber 46" equal to the suction in the supply tank before thesaid supply tank is connected therewith. By this construction, a returnsurge from the pressure and supply tanks is prevented and at the sametime the extraneous check valves are eliminated.

In Figs. 19 to 23 inclusive, there is illustrated means for adjustingthe throw of the pump rotor, which may be employed for compensating forslight inaccuracies in machining the parts in order to have the propertangential line contact between the said pump rotor and its housing, andmay also be employed for taking up wear between these parts. It will beunderstood that this adjusting mechanism is applicable to any type ofpump wherein a vane is employed for effecting the pumping operation, butfor convenience in illustration, use is made in the drawings of the pumpmechanism shown in Fig. 10, and enlarged for clear illustration.Accordingly, the pump rotor sleeve 41 has its bore slightly enlarged toaccommodate a sleeve I60 which is mounted about the eccentric portionI6I of the pump shaft I62. The pump shaft I62 has projecting from itsends the trunnion portions I63 and I64 which are formed around the axisof the pump drive shaft, of which the clutch I I4 is the only thingshown in Fig. 19. This axis is indicated by the point I65 in Figs.

20, 21 and 22. The shaft eccentric I6I is generated about an axis offsetwith respect to the axis for the shaft as a whole, and is indicated inFigs. 20, 21 and 22 by the reference character I66. The interior or bore.of the sleeve I60 is likewise generated about the axis I66 of the shafteccentric, while the exterior or outer surface of said sleeve isgenerated about an axis offset with respect to both the shaft axis I65and the shaft eccentric axis I66, and is indicated by a point by thereference character I61,

Extending through the lower end of the shaft I62 and the trunnion I64 isa bore receiving an oscillatable rod I68. from its upper end a headedscrew or shifter I89 which passes through a slot I10 in the shafteccentric I6I and is received in an aperture I1I formed in the sleeve.Secured to the lower end of the rod I68 is a wrench or lever I12 havingat its free end an elongated arcuate aperture I13 through which passes aclamp screw or bolt I14. The rod I68 below the screw I69 is hollow toreceive a tube I15 which forms the supply port for the pump and isconnected with the head I28 and supply conduit I21, and at its upper endforms the valve seat for the check valve 16, all

as disclosed in Fig. 10, and as above described.

The parts as illustrated in Figs. 19 and show them in normal position;that is, in pump operating position and with the pump rotor 41 havingtangential line contact with the pump housing sleeve 39. In order thatproper communication may be had between the pump chambers and thedischarge port 68 at the top of the shaft and with the supply port atthe bottom of the shaft, the eccentric sleeve I60 is provided withexterior circumferential grooves I16 and I11, respectively communicatingwith-one or more bores I18 and I19 formed through the sleeve and in turncommunicating with the grooves in the shaft eccentric which communicatewith a bore leading to the shaft supply and discharge ports. Should, forsome reason, the tangential line contact between the pump rotor and pumphousing be too great as with the parts as illustrated for example inFig. 20, it is only necessary to release the clamp The rod I68 hasprojecting bolt I14 and shift the lever I12 forwardly as seen in Fig. 19or in a counter clockwisedirection as seen in Fig. 23, for therebyrotating or oscillating the rod I68 and through its screw or shifter I69to shift the eccentric sleeve I60 in a clockwise direction as seen inFigs. 20 and 21 and thereby break or relieve the pressure at the pointof tangential line contact; As will be seen in Fig. 21, the parts are soillustrated that with the adjustment just described, a clearance,indicated by the reference character I in Fig. 21, may be obtained.Should now, with parts as illustrated in Figs. 19 and 20, the propertangential line contact not be established and a clearance exist. it isonly necessary to oppositely operate the lever I12 for shifting theeccentric sleeve I60 toward the position illustrated in Fig. 2-2, whichshows, by a dot and dash line, a portion of the inner wall of the pumpcylinder sleeve 39 as being taken or cut away by the pump rotor member41. In either position of adjustment, the lever I12 is then secured inposition by the clamp screw or bolt I14. It will be appreciated that theshaft I62 is held against lateral or rotative movement by the lever I24.

From the foregoing, it will be noted that the throw of the pump rotormay be adjusted to vary the pressure at the tangential line contact andto take up wear on these parts without interfering in any wise with theoperation of the pump.

In some instances, it may be desirable toautomatically adjust theposition of the rotor, as for example to relieve the pump of any contactof the rotor and its housing when starting the pump and subsequently toeffect this contact. In order to do this, a mechanism is illustrated inFigs. 24 and 25. As there shown, the clamping screw I14 is dispensedwith and the lever I12 has secured to it the inner ends I82 and I83respec tively of springs I84 and I85. The other end of the spring I84 issecured to a permanent anchor I86, while the other end of the spring I85is connected with the movable core I81 of a solenoid I88. The spring I84is utilized to shift the eccentric sleeve I60 and thereby the pump rotor41 to the position illustrated in Fig. 21, while the solenoid isemployed to shift these parts from this position to the desired pumpingcontact position which may be anywhere between the position shown inFig. 21 and that shown in Fig. 22 and passing through the position shownin Fig. 20. The spring I85 being employed to cushion the contact and toform a yielding connection and avoid excessive pressure at the line orpoint of tangential line contact, due to the pull of the solenoid.

In Fig. 25, there is diagrammatically illustrated an electric motorarmature I89 having associated therewith the starting and running fieldcoils I90 and I9I. The starting coils I90 have their opposite endsconnected with the power lines I92 and I93, with a cut-out switch I94connected therein and which switch is normally yieldingly closed asillustrated. The running coils I9I have their opposite ends likewiseconnected with the power lines I92 and I93, having imposed in thecircuit the coil of the switch opening solenoid I95. The closing of therunning coils circuit and likewise energization of the switch solenoidI95 completes a circuit through said switch, which includes the solenoidI88 for adjusting the position of the pump rotor.

The operation of this mechanism is as follows:

When the pump is stationary, the spring I84 actuates the lever I 12 to aposition for relieving all pressure between the pump rotor and itscylthereby shifting the pump rotor into contact with the housing.

With this construction, a motor may be employed having a, relatively lowstarting torque, which, when in operation, does the same amount of workand just as efficiently as the high-starting torque motor as heretoforeemployed.

From the foregoing, it will be seen that there has been provided a pumpor compressor mechanism in which the friction has been reduced to aminimum, since the only moving parts of the pump slide or oscillate onone another for a short distance, which is the difierence in thediameters of these parts, instead of having continuous sliding androtating surfaces throughout the peripheries, as is the case with theusual type of pump constructions. It will further be noted that thisresult is obtained whether the pump cylinder or the normal pump rotormember is the driven member of the unit. By this construction also,the-parts may be so arranged and assembled as to take up the smallestamount of space. It will further be appreciated that with theconstruction above the throw of the pump rotor is fully adjustable totake care of possible small errors in machining and to take up possiblewear between the pump housing and pump rotor.

What is claimed is:

her, a double hinge pump wing vbetweenfsaid pump .cylinder member androtor member-clividing the pump chamber into a suction chamber and a,compression chamber, a prime mover for effecting relative movementbetween the pump cylinder member and rotor member, and conduitsrespectively connected with the pump suction and compression chambersfor respectively supplying a medium'to be compressed and carry-. ing offthe compressed medium.

3. In a pump mechanism of the class described the combination of a pairof housing members adapted to be connected with each other forcompletely inclosing the pump mechanism and each having a bearinginalignment with each other, a pump cylinder member having at, its

1. In a pump mechanism of the class described I the combination of apairof housing members adapted to be connected with each other forcompletely inclosing the pump mechanism and each having a bearing inalignment with each other, a pump. cylinder member having at it'sopposite ends journals, journaled in the housing members bearings, apump rotor member within said cylinder member, a shaft having its endsjournaled in the pump cylindermember journals and having intermediateits ends an eccentric portion, said eccentric portion forming a journalfor and being encircled by the rotor member and the eccentricity of saidportion being such as to cause the rotor member to bear against and haveline contact with the inner peripheral wall of 'the pump cylindermember, a pump wing simultaneously hingedly connecting with the pumpcylinder member and rotor, and means for driving one of said pumpmembers.

2. In a pump mechanism of the class described the combination of a pairof housing members adapted to be connected with, each other forcompletelyinclosing the pump mechanism and each having a bearing inalignment with each other, a pump cylinder member having at its oppositeends journals, journaled in the housing members bearings, a pumprotormember within said cylinder member, a shaft having its ends journaled inthe pump cylinder member jour 'nals and having intermediate its ends aneccentric portion, said eccentric portion forming a journal for andbeing encircled by the rotor member and the eccentricity of said portionbeing such as to cause the rotor member to bear against and have linecontact with the inner peripheral wall of the pump cylinder memberthereby forming around the rotor a pump chamopposite ends journals,journaled in the housing members bearings, a pump rotor member withinsaid cylinder member, a shaft having its ends journaled in the pumpcylinder member journals and having intermediate its ends an eccentricportion, said eccentric portion forming a journal for and beingencircled by the rotor member and the eccentricity of said portion beingsuch as to cause the rotor member to bear against and have line contactwith the inner peripheral wall 'of the pump cylinder member therebyforming around .the rotor a pump chamber, a double hinge pump wingbetween said pump cylinder member and .rotor member dividing the pumpchamber into a suction chamber and a compression chamber, a prime moverfor efiecting relative movement between the pump cylinder member androtor member, conduits respectively connected with the pump suction andcompression chambers for respectively supplying a medium to becompressed and carrying off the compressed medium, means for supplyinglubricating -oil to the pump supply conduit for mixture with the mediumto be compressed, and means for removing the lubricating 'oil from thecompressed medium after it has passed through the pump compressionchamber.

4. In a mechanism of the class described the combination of a pair ofhousing support membersadapted to be connected to each other to form anhermetically sealed housing, said housing members each having a bearingboss in axial alignment with each other and respectively bored toprovide bearings, a motor field carried by one of the housing membersinteriorly thereof, a motor armature centrally of the field, a pumpcylinder sleeve, end plates carried by the pump cylinder sleeve andrespectively provided with bored journals, journaled in the housingbearing bosses, said pump cylinder sleeve and end plates forming the'means on which is mounted the motor armature laminations,'a shaftcentrally of the pump cylinder sleeve and journaled in the bores of theend plates journals, an eccentric on the shaft within the pump cylindersleeve between the end plates, a pump rotor journaled on the eccentricwhose eccentricity is such as to cause the pump rotor member to bearagainst and have line contact with the inner peripheral wall ofthe-cylinder sleeve to form around the rotor a pump chamber, a pump vanebetween the pump cylinder sleeve and pump rotor adapted to drive therotor by the sleeve around the shaft eccentric and said pane beingadapted to divide the pump combination of a pair of housing supportmembers adapted to be connected to each other to form and hermetically.sealed housing, said housing members each having a bearing boss in axialalignment with each other and respectively bored to provide bearings, amotor field carried by one of the housing members interiorly thereof, amotor armature centrally of the field, a pump cylinder sleeve, endplates carried. by the pump cylinder sleeve and respectively providedwith bored journals, journaled in the housing bearing bosses, said pumpcylinder sleeve and end plates forming the means on which is mounted themotor armature laminations, a shaft centrally of the pump cylindersleeve and journaled in the bores of the end plates journals, aneccentric on the shaft within'the pump cylinder sleeve between the endplates, a pump rotor journaled on the eccentric whose eccentricity issuch as to cause the pump rotor member to bear against and have linecontact with the inner peripheral wall of the cylinder sleeve to formaround the rotor a pump chamber, a pump vane between the pump cylindersleeve and pump rotor adapted to drive the rotor by the sleeve aroundthe shaft eccentric and said vane being adapted to divide the pumpchamber into a suction chamber and a compres-' sion chamber, meansproviding a source of supply of a medium to be compressed to the suctionchamber and storage for the compressed medium from the compressionchamber, said shaft being centrally bored from opposite ends to providea supply port and a discharge port respectively for the supply andcompression chambers, and one way check valves between the lastmentioned ports and the source of supply and storage.

6. In a mechanism of the class described the combinatipn of a pair ofhousing support members adapted'to be connected to each other to form anhermetically sealed housing, said housing members each having a bearingboss in axial alignment with each other and respectively bored toprovide bearings, a motor field carried by one of the housing membersinteriorly thereof, a motor armature centrally of the field, a pumpcylinder sleeve, end plates carried by the pump cylinder sleeve andrespectively provided with bored journals, journaled in thehousing'bearing,

bosses, said pump cylinder sleeve and end plates forming the means onwhich is mounted the motor armature laminations, a shaft centrally ofthe pump cylinder sleeve and journaled in the bores of the end-platesjournals, an eccentric on the shaft within the pump cylinder sleevebetween the end plates, a pump rotor journaled on the eccentric whoseeccentricity is such as to cause the pump rotor member to bear againstand have line contact with the inner peripheral wall of the cylindersleeve to form around the rotor a pump chamber, a pump vane between thepump cylinder sleeve and pump rotor adapted to drive the rotor by thesleeve around the shaft eccentric and said vane being adapted to dividethe pump chamber into a suction chamber and a compression chamber,mea'ns providing a source of supply of a medium to be compressed to thesuction chamber and storage for the compressed medium from thecompression chamber, lubricant storage means within the inclosinghousing, and means for supply said lubricant to the medium as it passesbetween the supply source and pump suction chamber.

combination of a pair of housing support members adapted to be connectedto each other to form an hermetically sealed housing, said housingmembers each having a. bearing boss in axial alignment with each otherand respectively bored to provided bearings, a motor field carried byone of the housing members interiorly thereof, a motor armaturecentrally of the field, a pump cylinder sleeve, end plates carried bythe pump cylinder sleeve and respectively provided with bored journals,journaled in the housing bearing bosses, said pump cylinder sleeve andend plates forming the means on which is mounted the motor armaturelaminations, a shaft centrally of the pump cylinder sleeve and journaledin the bores of the end plates journals, an eccentric on the shaftwithin the pump cylinder sleeve between the end plates, a pump rotorjournaled on the eccentric whose eccentricity is such as to cause thepump rotor member to bear against and have line contact with the innerperipheral wall of the cylinder sleeve to form around the rotor a pumpchamber, a pump vane between the pump cylinder sleeve and pump rotoradapted to drive the rotor by the sleeve around the shaft eccentrio andsaid vane being adapted to divide the pump chamber into a suctionchamber and a compression chamber, means providing a source of supply ofa medium to be compressed to the suction chamber and storage for thecompressed medium from the compression chamber, lubricant storage meanswithin the inclosing hous- -ing, means for supplying said lubricant tothe medium as it passes between the supply source .sleeve member, a pumprotor member, a shaft mounted concentrically with respect to the pumpcylinder sleeve member and having an eccentric portion within the pumpcylinder sleeve on which is journaled the pump rotor and theeccentricity being such as to eccentrically arrange the pump rotor withrespect to the pump cylinder sleeve so as to have tangential linecontact between the pump cylinder sleeve member and rotor member, .saidpump members being 'so mounted for rotation as to have one of themdriven around the axis of the shaft, an electric motor connected withsaid one driven member to effect its drive and rotation, means forchanging the eccentric throw of the shaft and thereby changing theeccentric arrangement of the pump cylinder sleeve member and pump rotormember including a sleeve journaledon the shaft eccentric, said shafteccentric sleeve having an outer surface developed about an axiseccentric to the axes of the shaft and its eccentric, an arm forrevolving the shaft eccentric sleeve around the shaft eccentric to addor subtract its eccentricity to that of the shaft eccentric and therebychange the throw of the shaft eccentric, spring means for actuating thearm to subtract the sleeve eccentricity from the shaft eccentricity, andelectro-magnetic means operable with the pump member driving electricmotor for adding the sleeve eccentricity to the shaft eccentricity.

JESSE s. WENTWOR'IH.

